EP1714091B1 - Defrost mode for hvac heat pump systems - Google Patents
Defrost mode for hvac heat pump systems Download PDFInfo
- Publication number
- EP1714091B1 EP1714091B1 EP05713076.7A EP05713076A EP1714091B1 EP 1714091 B1 EP1714091 B1 EP 1714091B1 EP 05713076 A EP05713076 A EP 05713076A EP 1714091 B1 EP1714091 B1 EP 1714091B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- defrost mode
- refrigerant
- heat exchanger
- evaporator
- water
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/13—Mass flow of refrigerants
- F25B2700/133—Mass flow of refrigerants through the condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Air Conditioning Control Device (AREA)
Description
- This invention relates to several improvements for determining when to initiate a defrost mode for a heat pump, and also to protect associated systems such as a hot water supply system during a defrost mode.
- Heating, ventilation and air conditioning (HVAC) systems are utilized to provide cooling and heating in buildings. Typically, a compressor delivers a refrigerant to a heat exchanger which is a heat exchanger associated with the interior of a building. The refrigerant passes to an expansion device downstream of the heat exchanger, and downstream of the expansion device to an evaporator. The evaporator is typically a heat exchanger that exchanges heat with an outside environment.
- When an HVAC system is utilized to provide heating, it can be said to be in a heat pump mode. Under such conditions, the evaporator may be in a very cold environment, such as during winter. Problems can arise in that frost can form on the evaporator heat exchanger coils. This lowers the ability to transfer heat from the system to the outside environment through the evaporator heat exchanger.
- Thus, such systems have a defrost mode. In defrost mode, the hot refrigerant leaving the compressor is bypassed directly to the evaporator. The bypass can occur by reducing the removal of heat in the heat exchanger, or can be a bypass of some refrigerant around the heat exchanger. To date, there has been little in the way of sophisticated control to determine how and when the defrost mode should be actuated.
- Moreover, when a heat pump system is utilized to heat water, such as for a hot water heating system, problems can arise during defrost mode. In particular, defrost mode is often utilized in combination with shutting down the pumping of water through the heat exchanger. This is done since if the water continues to flow, the refrigerant will be cooled in the heat exchanger. Under such conditions, the water that sits in the heat exchanger can boil, which would be undesirable.
- Another problem can occur near the end of a defrost mode. At this point, the bulk of the frost will have melted. There are water droplets remaining on the coil. Since the fan is turned off, there is no air removing these droplets. Leaving the droplets on the coil increases the likelihood that the coil will quickly frost again after the termination of the defrost mode. Further, since the fan is not driving air over the coil, little heat is being removed from the refrigerant in the coil. Thus, the refrigerant temperature exiting the evaporator remains higher than might be desired.
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US 5438844 ,EP 0271428 andUS 4373349 disclose a heat pump cycle of the type defined in the preamble of claim 1. - The invention provides a heat pump cycle as defined in claim 1.
- Moreover, protection for the water remaining in the heat exchanger during a defrost mode is also disclosed. The protection may take the form of periodically operating the water pump during defrost mode to remove the water in the heat exchanger such that it is not subject to the high refrigerant heat for an undue length of time. Alternatively, the water pump may not be stopped until the refrigerant temperature is lowered to a point such that the water would tend not to boil. That is, some method for beginning to lower the refrigerant temperature at the compressor outlet can be initiated such that before the water pump is stopped, the refrigerant temperature has lowered below the boiling point of water.
- Another feature is utilized, particularly near the end of a defrost cycle, to blow air over the evaporator coils. Typically, during a defrost cycle, the fan is stopped, as blowing air over the evaporator coils tends to remove heat to the air which would be better utilized to melt the frost. However, by beginning to utilize the fan at least near the end of the defrost cycle, the melted water droplets can be taken away. Moreover, as the water begins to melt, if the temperature is not lowered, such as by air, the temperature of the refrigerant leaving the evaporator can begin to reach unduly high temperatures. This could result in problems elsewhere within the system.
- Finally, a number of distinct system variables are disclosed as being useful for identifying when to begin and end a defrost cycle.
- These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
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Figure 1 is a schematic view of a heat pump system for providing heated water. -
Figure 2A is a graph of capacity for the inventive system. -
Figure 2B is a graph of a system condition. -
Figure 3A shows a flow chart for a control feature. -
Figure 3B is a flowchart of the inventive system. - A heat pump cycle 20 is illustrated schematically in
Figure 1 . As known, acompressor 22 compresses a refrigerant and discharges the refrigerant downstream towardheat exchanger 32. As shown, a sensor 24 is positioned on this downstream line. Further, avalve 26 selectively allows the flow into abypass line 28, which will bypass a portion of the refrigerant to a downstream point 30, bypassing theheat exchanger 32.Bypass line 28 is optional, and is a component to provide a defrost function as will be explained below. Ahot water line 34 passes in heat exchange relationship with the refrigerant in theheat exchanger 32. Ahot water pump 36 drives the flow of the water through theheat exchanger 32. - An
expansion device 38 is positioned downstream of theheat exchanger 32, and anevaporator 40 is downstream of theexpansion device 38. Typically, theevaporator 40 includes heat transfer coils. Afan 42 blows air over theevaporator 40 to heat the refrigerant in the evaporator. Downstream ofevaporator 40, the refrigerant returns to thecompressor 22. As shown, asensor 44 may be optionally positioned to sense a condition of the refrigerant approaching thecompressor 22. - As known, the heat pump cycle 20 operates to heat water in the
water supply line 34. Refrigerant is compressed atcompressor 22, and is hot when enteringheat exchanger 32. Inheat exchanger 32, this hot refrigerant transfers heat to the water inwater supply line 34.Pump 36 drives the water through theheat exchanger 32, and to a downstream use for the hot water. The refrigerant leaving theheat exchanger 32 is expanded by theexpansion device 38, and then passes to theevaporator 40, and heat is transferred with the outside environment atevaporator 40. - The present invention is directed to solving some challenges in operating the cycle 20. In particular, the
evaporator 40 is outside and exposed to the environment. During cold temperature, frost may accumulate on the heat transfer coils. This reduces the ability to remove heat from the refrigerant in theevaporator 40, and thus lowers the capacity of system 20 to deliver heat to thehot water 34. Thus, defrost modes are known. - In a defrost mode, hot refrigerant is directed through the
evaporator 40 to melt the frost. The hot refrigerant is delivered to theevaporator 40 in one of two basic ways in the prior art. First, thevalve 26 may be opened to bypass refrigerant throughline 28 and around theevaporator 32. Typically, not all of the refrigerant is bypassed, and some does continue to move through theevaporator 32. Alternatively, (or in conjunction with the bypass), thepump 36 may be stopped. Since water is no longer driven through the heat exchanger, the refrigerant passing through the heat exchanger tends to remain hot. Thus, hot refrigerant approaches theevaporator 40. Typically, in the prior art defrost mode, thefan 42 is also stopped during the defrost mode. - As mentioned above, there are design challenges with the defrost mode. In particular, the defrost mode has typically not been operated in a very efficient manner. There are also challenges with regard to unduly heating water in the
line 34 during defrost mode, and also resulting in unduly high refrigerant temperature leaving theevaporator 40 as the defrost comes to a close and the frost has all been melted. -
Figure 2A schematically shows the quantity of heat that can be delivered into the water by the system 20, and how that quantity would change with time. As shown, periodically, defrost modes are initiated. There is little or no heat transfer during a defrost mode typically. Thus, the defrost mode itself lowers the total heat flow into the water. On the other hand, as can be appreciated from the graph, with time, the quantity of heat delivered into the water drops as frost builds up on theevaporator 40. The present invention seeks to maximize an average heat transfer QAVG by optimizing the timing of the defrost mode to ensure maximum heat transfer. - As shown in
Figure 2B , some system quantity such as the difference between outdoor temperature and the temperature sensed bysensor 44 may be experimentally plotted against the quantity of heat provided. As can be seen inFigure 2B , the heat transfer provided will drop off as the difference between outdoor temperature To and the temperature at sensor 44 TX increases. That is, as frost builds up on the evaporator, the temperature of the refrigerant in the evaporator tends to be reduced less than if good heat transfer were occurring. A plot such as shown inFigure 2B is developed experimentally and then utilized to maximize the average heat transfer such as is illustrated inFigure 2A . Generally, if the defrost cycles are too frequent, then the system loses available heat transfer. On the other hand, if the defrost cycles are too infrequent, the slope of the heat transfer drops off such that little heat transfer is occurring. Thus, a chart such as utilized inFigure 2A is used in conjunction with the concepts illustrated inFigure 2B to maximize QAVG. A worker of ordinary skill in the art would recognize how to perform such a maximization. - Assuming that the graph of
Figure 2A is an optimum cycle, a point X can be shown which would be the optimum point to initiate a defrost mode. A system monitoring some system condition will associate that system condition with point X. - The system condition utilized to define point X can be any one of several. For example, the temperature difference between outdoor air and the refrigerant at the low pressure side (i.e., as sensed by sensor 44) can be utilized to determine defrost initiation, and monitored to identify when the circuit has reached point X. When the temperature differential exceeds a defrost initiation value, then defrost operating mode is initiated. Also, the temperature of the refrigerant at
sensor 44, or elsewhere on the low pressure side, can be used to determine defrost initiation. When this temperature drops below a defrost initiation value, then point X may be identified, and defrost mode initiated. - Further, the pressure of the refrigerant on the low side, or at
sensor 44 can be utilized to determine point X and initiate defrost. When the pressure drops below a defrost initiation value, defrost mode may be initiated. Also, the water flow rate through thesensor 32 can be utilized to identify point X, and begin defrost operating mode. Similarly, if thewater pump 36 is variable speed, the control signals can be utilized to determine defrost initiation. A system co-efficient of performance can be utilized to determine defrost initiation. The co-efficient of performance can be monitored, and when it drops below a defrost initiation value, defrost mode may be initiated. - Point Y can be determined based upon several system conditions also. As an example, the temperature of the refrigerant at
sensor 44 may also be utilized to determine defrost conclusion. When the temperature exceeds a defrost conclusion value, defrost operating mode can be concluded and point Y identified. Also, the pressure of the low side refrigerant can be utilized to determine point Y, and defrost conclusion. As one further example, the temperature difference between the refrigerant on the low side (i.e., center 44) and outdoor air temperature can be utilized to determine defrost conclusion. When this temperature differential exceeds a defrost conclusion value, defrost operating mode may be concluded. - When the system reaches point X, then defrost mode is initiated. When defrost mode ends, the system condition reaches point Y. Again, these conditions could be developed experimentally.
- Further, the duration of the defrost mode could simply be based upon a timer. In this sense, the "approaching the end" of defrost mode would simply be based upon expired time. Also, some of the above-referenced methods, such as the protection to minimize the likelihood of water being unduly heated in the heat exchanger, or the operation of the fan, could extend to the existing defrost modes, wherein the defrost is simply actuated such as periodically, etc.
- As mentioned above, during defrost mode, the
water pump 36 is typically stopped. Thus, water is not moving through the heat exchanger inline 34, but instead a quantity of water remains stored in the heat exchanger. This water could be superheated to a boiling point if left alone. The present invention thus protects against unduly hot water. Two methods have been developed. First, thewater pump 36 may be periodically run during defrost mode to move the water through the heat exchanger. Thus, while the water pump will generally be stopped for the bulk of the time during defrost mode, it will be intermittently run such that the water is cycled through the heat exchanger. This will prevent the water from becoming unduly hot. - The second method of preventing the water from boiling may be used alternatively, or could be used in conjunction with the periodic running of the water pump. In the second method, the
sensor 44 senses the pressure or temperature of the refrigerant downstream ofcompressor 22. Thewater pump 36 is not stopped in defrost mode until that discharge refrigerant quantity drops to a predetermined amount which would be indicative of the refrigerant temperature being below the boiling point of the water in theline 34. As known, the pressure or temperature can be reduced by opening theexpansion device 38 to lower the pressure approaching the compressor, and hence the discharge pressure. By so doing, the present invention ensures that when thewater pump 36 is stopped, the temperature of the refrigerant will be sufficiently low (i.e., below the boiling point), and the problem mentioned above will not occur. - As shown in
Figure 3A , a control for performing the above temperature adjustment steps asks if the temperature of the refrigerant at the discharge of the compressor is too high. If not, then the defrost mode may be actuated. If the temperature is too high, then a lower target discharge pressure is determined which will in turn result in a lower compressor discharge temperature. A second control loop receives that target discharge pressure, and compares the actual discharge pressure to the target. If the actual discharge pressure meets the target, then the flow chart returns to the first control loop to compare the actual refrigerant discharge temperature to the target. However, if the actual discharge pressure is different than the target, then the expansion device is controlled with known algorithms to achieve a new pressure. The use of this dual or nested control loop achieves a smoother change in the pressure, which will eliminate sharp pressure pulses. Moreover, the dual loop assures that the temperature can be accurately maintained very close to the target temperature, while still insuring the target temperature is not exceeded. - Another feature of a defrost mode is that the
fan 42 is typically stopped. As mentioned above, there are problems with this in that the water droplets of the melted frost remain on the heat transfer fins, and could easily frost again once defrost mode is stopped. Moreover, as the defrost mode approaches its end, too little heat is being removed from the evaporator in that air is not being driven over the fins. Thus, the refrigerant pressure and temperature approaching the compressor become unduly high, and can result in additional system problems. One control option to address this concern is to further open theexpansion valve 38 to lower refrigerant temperature. However, under some system conditions, this would require an unduly large expansion valve that would add to costs. - Thus, the present invention avoids the problem of undue refrigerant temperature or pressure downstream of
evaporator 40. Most preferably, when it is learned that the defrost mode is nearing its end, thefan 42 is started. Preferably, a control monitors the system condition that is being monitored to identify point Y. As the condition approaches Y and is within some predetermined amount, the control will begin operation offan 42, as it senses the defrost mode is nearing a conclusion. This provides two benefits. First, the water droplets which are melted on the heat transfer coils, etc., are removed by this air being blown over them. Secondly, the refrigerant is cooled by the flowing air, and does not approach unduly high pressures or temperatures. - As shown in
Figure 3B , a flowchart of this invention includes the steps of first determining the best average time and spacing for the defrost cycle, that is the charts such as shown inFigure 2A . Second, the system condition is monitored, and when the point X is reached, defrost mode is initiated. During defrost mode, water boil protection occurs. Finally, when it is determined that defrost mode is approaching its end point (Y), the fan is turned on. - Each of the several features mentioned above can be utilized in combination or separately. Controls for controlling all of the various components in the cycle 20 are known. Such controls are operable to control the various components. A worker of ordinary skill in the art would recognize how to provide control to achieve the above-referenced methods and functions.
- Although a preferred embodiment of this invention has been disclosed, a worker of ordinary skill in this art would recognize that certain modifications would come within the scope of this invention. For that reason, the following claims should be studied to determine the true scope and content of this invention.
Claims (5)
- A heat pump cycle comprising:a compressor (22) for compressing a refrigerant;a heat exchanger (32) downstream of said compressor (22);a main expansion device (38) downstream of said heat exchanger (32);an evaporator (40) downstream of said main expansion device (38), and a refrigerant flowing from said compressor (22) to said heat exchanger (32), to said expansion device (38), to said evaporator (40), and returning to said compressor (22),a fan (42) for blowing air over said evaporator (40);a hot water supply to be heated in said heat exchanger (32) and a water pump (36) for moving water through said heat exchanger (32); anda control for said cycle, said control being operable to control components and initiate a defrost mode at which refrigerant from a discharge side of said compressor (22) is cycled into said evaporator (40) at a relatively hot temperature to defrost said evaporator (40), said control being operable to initiate said defrost mode based upon an algorithm developed to maximum heat transfer from said heat pump to an environment to be heated,characterised by: said control also being operable to stop said water pump (36) during defrost mode and operates to minimize the likelihood of water in said heat exchanger (32) being unduly heated during defrost mode, said control also stopping said fan (42) during defrost mode, and monitoring system conditions to identify an approaching end of said defrost mode, and actuating said fan (42) to begin blowing air over said evaporator (40) prior to an end of said defrost mode.
- The cycle as set forth in claim 1, wherein said water pump (36) is actuated intermittently to minimize said likelihood.
- The cycle as set forth in claim 1, wherein said water pump (36) is stopped during defrost mode, but said water pump (36) does not stop until said control has determined that a discharge temperature of said refrigerant has dropped below a predetermined maximum to minimize said likelihood.
- The cycle as set forth in claim 3, wherein an actual discharge temperature is compared to said predetermined maximum, and if said actual discharge temperature exceeds the predetermined maximum, a new target pressure is determined, and said control controlling said expansion device to achieve said new target pressure.
- The cycle as set forth in claim 1, wherein said defrost mode includes opening a bypass (28) to bypass a portion of a refrigerant downstream of said compressor (22) around said heat exchanger (32).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/776,374 US7228692B2 (en) | 2004-02-11 | 2004-02-11 | Defrost mode for HVAC heat pump systems |
PCT/US2005/003902 WO2005077015A2 (en) | 2004-02-11 | 2005-02-07 | Defrost mode for hvac heat pump systems |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1714091A2 EP1714091A2 (en) | 2006-10-25 |
EP1714091A4 EP1714091A4 (en) | 2009-10-28 |
EP1714091B1 true EP1714091B1 (en) | 2016-12-14 |
Family
ID=34827367
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05713076.7A Not-in-force EP1714091B1 (en) | 2004-02-11 | 2005-02-07 | Defrost mode for hvac heat pump systems |
Country Status (6)
Country | Link |
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US (2) | US7228692B2 (en) |
EP (1) | EP1714091B1 (en) |
JP (1) | JP2007522430A (en) |
CN (1) | CN100467981C (en) |
HK (1) | HK1103248A1 (en) |
WO (1) | WO2005077015A2 (en) |
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2004
- 2004-02-11 US US10/776,374 patent/US7228692B2/en not_active Expired - Fee Related
-
2005
- 2005-02-07 CN CNB2005800044009A patent/CN100467981C/en not_active Expired - Fee Related
- 2005-02-07 WO PCT/US2005/003902 patent/WO2005077015A2/en active Application Filing
- 2005-02-07 JP JP2006553182A patent/JP2007522430A/en active Pending
- 2005-02-07 EP EP05713076.7A patent/EP1714091B1/en not_active Not-in-force
-
2007
- 2007-05-04 US US11/744,339 patent/US7707842B2/en active Active
- 2007-07-17 HK HK07107646.6A patent/HK1103248A1/en not_active IP Right Cessation
Non-Patent Citations (1)
Title |
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None * |
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US7228692B2 (en) | 2007-06-12 |
EP1714091A2 (en) | 2006-10-25 |
WO2005077015A2 (en) | 2005-08-25 |
US7707842B2 (en) | 2010-05-04 |
JP2007522430A (en) | 2007-08-09 |
CN100467981C (en) | 2009-03-11 |
EP1714091A4 (en) | 2009-10-28 |
CN1918437A (en) | 2007-02-21 |
HK1103248A1 (en) | 2007-12-14 |
US20070204636A1 (en) | 2007-09-06 |
WO2005077015A3 (en) | 2006-04-20 |
US20050172648A1 (en) | 2005-08-11 |
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